Refrigerating machine



Feb. 9, .1932. c. P..BRocKwAY 1,844,029

REFRIGERATING MACHINE Original Filed July 27, 1921 l 5 Sheets-Sheet 1 INVENTOR. Car/ P Brockway ATTORNEYS.

Feb. 9, 1932.

c. P. BRocKwAY 1,844,029

REFRIGERATING MACHINE V Original Filed July 27, 1921 5 Sheets-She??l 2 IN VEN TOR. 6dr/ .P .Eroc/r way ATTORNEYS.

Feb. 9, 1932. c. P. BROCKWAY 1,844,029

REFRIGERATING MACHINE Original Filed July 27, 1921 5 lSheets-Sheet 5 I I I' I .L-lJ' INVENTOR.

Carl P roc/rwa) i l V z n ATTORNEYS.

Feb. 9, 1932. c. P. BROCKWAY REFRIGERATING MACHINE Original Filed July 27, 1921 5 Sheets-Sheet 4 INVENTOR. ar/ E Brockway A TTORNEYS. l

Feb. 9, 1932.

C. P. BROCKWAY REFRIGERATING MACHINE Original Filed July 27, 1921 5 sheets-sheet 5 Gf/ P foc/rway ATTORNEYS.

Patented Feb. 9, 1932 UNITED STATES PATENT OFFICE CARL P. BROCKWAY, OF PATERSON, NEW JERSEY, ASSIGNOB, BY MESNE ASSIGNMENTS, TO THE TILLOTSON MANUFACTURING COMPANY, OF TOLEDO, OHIO, A CORPORATION 0F DELAWARE BEFRIGERATING MACHINE Application led July 27, 1921, Serial No. 487,973. Renewed January 16, 1929.

The present invention relates to an improved refrigeration method and apparatus operating upon the principle of the compression and expansion of a suitable refrigerant contained in a preferably sealed enclosing means, involving and including in the action thereof a large increase in the efficiency of the transfer of heat particularly to the expanding refrigerant from the medium directly cooled or refrigerated thereby. The invention may also include features materially aiding expansion of the refrigerant in the expansion chamber.

' Besides the method, the invention has f'or its object to provide a novel apparatus whereby the action of the refrigerant which is enclosed as indicated and which is caused to expand and rapidly absorb heat, is particularly eflicient whereby a higher speed in action and a smaller unit as a whole may be used.-

Further objects of the invention relate to a novel method and an apparatus of the character indicated which may be obtained without the need of lubricant and refrigerant separation because of the efficient operation of the system and the novel means for withdrawing lubricant from the expanding chamber.

Further objects of the invention are to provide for the joint utilization of evaporating and heat transferring means in the expansion chamber; a novel construction of heat transferring means which rapidly conduct the heat from the surrounding medium to the expanding refrigerant; a novel construction of refrigerant expansion chamber with integral heat dissipating fins for use in cooling both a liquid such as brine or air where the expansion chamber may be made of sheet metal stampings and suitably assembled to provide the suitable heat transferring structure hereinbefore referred to.

Further objects and those relating to simplicity of structure and economies of manufacture will appear as I proceed with a detailed description of my invention illustrated in the accompanying drawings in which Figure I is a view of the present invention as applied to a refrigeration system;

Figure II is a longitudinal sectional view of one embodiment of my invention;

Figure III is a sectional view taken on line III- III of Figure II showing a form of compresslon pump;

Figure IV is a sectional view of a modified embodiment of my invention;

Figure V is a sectional view of another modified embodiment of the invention while,

Figures VI, VII, VIII and IX are views showing details of construction of the eX- panding chamber and heat transferring means employed in the present invention, and

Figure X is a sectional view showing an arrangement in which the compression chamber is air cooled and in which the refrigerating chamber is constructed of a'plurality of sheet metal stampings for use where the refrigerant cools alr, for example, instead of liquid.

Referring to Figure I it will be seen that the present invention includes the use of a sealed compression and condensing chamber 10 and a similarly sealed expansion chamber 11 adapted to be rotated as a unit whereby gas from chamber 11 is compressed and condensed in chamber 10 and then permitted to pass back to chamber 11 and evaporate therein to refrigerate a conducting medium. In this connection there is shown an enclosure 12 around the compression chamber 10 adapted to form means whereby a cooling liquid such as water may circulate, thus forming the means for the ultimate dissipation of the heat. For the purpose of illustration, I have shown a receptacle 12 as provided with a water inlet 13 terminating in a spray pipe 14 positioned above the compression chamber 10 and extending the major portion of its length. A Water outlet 15 is positioned in the end of tank 12 at a point suiiiciently elevated as to permit water to contact with the compression chamber 10. The expansion chamber l1 is located in a tank 17 in which brine or other suitable fluid may be caused to pass and be cooled by the expansion of the refrigerant in the expanding chamber 11. A suitable motor 20, Flgure I, may be directly connected with the tank 10 to rotate both the sealed tanks 10 and 11 in unison, the

Atwo hollow castings and 31 provided at their adjoining edges with outwardly offset overlapping portions 32 and 33 to form an annular channel 34, the sections 30 and 31 being sealed together at the joint 35 as shown. The expansion tank 11 may likewise be cast in two sections 36 and 37, sealed together at 38 while the two tanks 10 and 11 are connected by a Coupling member 4() which may be integral with one or both the tanks or secured to each in any suitable sealed manner. The connector 40 forms a hub which may be provided with the bushings 41 revolving in the bearing 21 as heretofore indicated.

Within the compressor 10 any suitable means for compressing the fiuid drawn therein from tank 11 may be employed, there being illustrated a rotary gear pump having a. gear and complementary gear 51', the gear 50 being keyed to the rotating shaft which may constitute an integral connection with the connector 40, while the gear 51 is held from revolving by being pivotally connected with a suitable weight 58 swung from the ball bearings 59 and 60 thereby always maintaining a fixed position for the gear 51. Thus the rotation of the unit as a whole causes the rotation of the gear 50 which in turn rotates the gear 51 effecting the operation of the gear pump mechanism, the bearings 59 and 60 riding respectively on the hub 40 and a stub shaft 61 at the other end of the casing 10. They gear chamber may be provided with a suitable enclosing casing 65.

Extending through the connector 40 is a tube 68 through which the expanded gas may be drawn by the gear pump. This tube may be a single member mounted loosely in the hub 40, or a divided member interconnected at a gas proof joint 70, as shown, the part 71 moving with the hub and the part 72 stationary with the gear chamber 65. In either arrangement, it is essential that a free connection facilitated by the use of bearings 73, be maintained between the hub of gear 50 and the part 72.

From the compressor end of the tube 68.l

the gas is led through a pipe 7 4 to the inlet port 75 (F ig. III) of the gear pump and thence to an outlet pipe 76 discharging into the open chamber 10.

A suitable pipe 77 terminates in the annular channel 34 of the compressor chamber 10 and passes through the connector -40 discharging in the nozzle 78 and expansion chamber 11. If desired a controlling valve 79 shown in Figure V may be employed to prevent passage of compressed refrigerant through the pipe 77 until the desired pressurel has been attained.

Attention is called to the fact that each of the chambers 1() and 11 are elongated and of relatively small diameter which has the important function of permitting a relatively high speed of rotation without the objectionable feature of a large diameter and at the same time providing a larger surface in contact with air for the transfer 0f heat both from the compressor to the cooling water and to the expansion chamber from the fluid or liquid to be cooled.

The construction of the expansion tank 11 constitutes an important feature of the invention as each of the sections 36 and 37 are provided with suitably spaced heat conducting ribs 8O extending internally of the tank 11. Suitable transverse openings 81 may be formed in each of the ribs 80 to permit excess of unexpanded refrigerant and mixture of lubricating oil, if employed, to flow along the periphery of the tank 11. The ribs 8O as i1- lustrated extend around the entire periphery internally of the chamber 11 and are adapted to extend through any film of liquid refrigerant or emulsion thereof with a lubricating oil into the expanding gas within the expansion chamber to thereby form means for transferring heat from a medium located outside the expansion chamber to the interior active part of said chamber. It will be noted that the chamber 11 illustrated is in the form of a cylinder so that there will tend to be a film of liquid around the entire interior cylindrical wall thereof of a substantially uniform depth so that each of the ribs 80 would be practically the same height above the liquid. Should any other form of chamber be chosen or for any other reason should there tend to be a greater accumulation of liquid on the interior v periphery of the drum 11, the heighth of the heat transferring ribs above the liquid film would of course vary.

The importance of the use of the above described ribs 80 will be appreciated when it is understood that their employment does away with the necessity of separating the oil lubricant from the refrigerating fluid and return the ribs 80, however, heat is conducted directly through this film from the brine or atmosphere to the tank interior and eva orization is carried on whether or not an oil 1m has been formed in the tank. It is therefore-apparent, because of the 4use of the ribs 80, that no real necessity arises for returning lubricant to the condenser chamber only as is required for proper lubrication and sealing of the compressor pump. In fact if more than this required amount is returned it merely increases the work of the pump and hinders the refrigerating action of the refrigerating fluid by Aflowing through the refri erantpipe. 77 so that the general efficiency o the system is materially diminished.

Means for returning a restricted amount of oil for sealing and lubricating purposes is illustrated in a pipe 85 terminating at 86 adjacent the periphery of the tank 11 on one end and at 87 at the other end, in the connecting passage 68 through which the expanded gas is drawn into the compressor. The amount of lubricant returned is limited not only by thev cross section of the pipe 85, but also by the injector arrangement of the end 87 in the passage 68, the suction effect of which may be varied by changing the external cross-section of the end 87 or varying its position axially within the passage 68. v.

It should be noted that the depth of the oil level in the expansion tank 11 is imma'- terial in its eect on the rate of oil return to the pump, and further, that the rate of return, through the injector action just described, varies with the relative tank pressure and therefore with the actual requirements of the pump, thus resulting in highest eiiciency. In ordinary running conditions, and especially when external temperatures are hi h, and theA refrigerator is operating at ful capacity,

there is no accumulation of refrigeratingfluid as a liquid in the expansion tank 11 due to the enlarged heat capacity of the system, but at starting and at the lower external temperatures there may be a small accumulation of the refrigerant'as a liquid between the oil film, if such has been formed, and the tank wall. In this formation, free evaporization of the liquid refrigerant 1s hindered and it is therefore desirable to provide means for agitating the film surface to some extent.

In the embodiment illustrated in Figurey V the expansion tank 11 is provided with means for causing the agitation of the liquid which tends to collect on the periphery of the chamber. A. convenient arrangement consists in providing a plurality of weights 90 which may be arrangedto remain stationary in the rotating tank as, for example, when hung from a bearing sleeve 91 mounted on a pin 92 which is screw threaded from the inside of the tank 11 into a suitable receiving hub 93. These dependin arms 90 are interposed between the heat dissipating ribs 80 as indicated and between the ribs and the wall of the expansion tank. In the embodiment illustrated in Figure V, the pipe 77 which conducts the refrigerant from the compression chamber 10 to the expansion chamber 11 is open at the end in the compression tank 10 and is provided with pressure controlling expansion valve 79 at the other end in the expansion tank 11. There is illustrated for this valve member a bracket 63 carrying a slidable valve pin 64 controlled by the spring the pressure of which may be predetermined to cause the Valve 64 to open when the pressure in the pipe 77 exceedsan `amount limiting thefminimum pressure for inost effective operation.

In Figure V, moreover, is illustrated structural modifications of the connections and pump suspension, consisting in an arrangement whereby the gear .50 is held from rotation while the gear 5l is bodily moved around the gear 50. In the accomplishment of this modification the gear 51 'is mounted on a pin 95 secured to the inner head 96 of the compressor, the gear 50, also having a free support on the compressor head by means of a stub pin 97, but rigidly secured as regards rotation by means of an axial shaft extension 98 to the non-rotating Weight 99. Thus the gear 50 is held from rotation while the gear 51 is carried bodily about the gear 50 through the rotation of the compressor. The plate 100, fixed in any suitable manner to the compressor head, forms a bearing support for the gear pin 95 and 98, and also through ball bearings 101, for one end of the weight 99, the other end of which weight being supported from the stub shaft 102 through bearings 103.

In this modification it should be noted further that the inlet conduit from the expander to the compressor is a tube'104 drilled or otherwise formed in the solid hub 105 integral with the compressor end 96 so that the possibility of gas leakage at this point is a minimum. The surplus drainage pipe 106 has one end 107 terminating within this tube and the other end 108 terminating near the periphery of the expander at a. polnt predetermined to give a most effective depth of cooling liquid and to remove proper amounts of lubricant. This point should be slightly inward from the end 109 of the splash Weights 90.

Figure IV illustrates an embodiment of my invention wherein the inlet pipe 110 from the expander to the compressor has capacity sufficient to contain the outlet pipe 111 from the compressor to the expander, the latter pipe extending along the rotational axis of the unit, one end 112 terminating adjacent the periphery of the compressor 10 and the other end 113 extending out into the expander chamber toward the wallthereof. The pump suspension is similar in this modication to` the disclosure of Figure II, the gear 51 being mounted for non-bodily movement.

A further modified form of the invention is disclosed in Figure X of the drawings. In this arrangement the relative relationship of pipes 110 and 111, as disclosed in Figure IV are reversed, the outlet pipe 114 being designed to include the inlet pipe 115. To take care of this structure the pipe 114 is extended from the hub 40 to the stub shaft 116 on the opposite side of the compressor, and loosely seated in a depression 117 formed therein. A depending pipe 118 extends from the pipe 114 to the compressor periphery. The expander end of the pipe 114 is constricted about the inlet pipe 115 thereby forming a nozzle exit for the compressed fluid. The pipe 115 extends into the expansion chamber to a point adjacent the periphery thereof.

The modification of Figure X further exemplifies the application of my invention to air cooling, both as regards cooling of the compressor and cooling by the expander. To effect this result the compressor casing 12o is formed with heat radiating ribs 121 which afford the requisite radiating area for the heat generated through the compression process. In addition the expansion chamber 122 is formed not only with internal ribs 123 but also with external ribs 124 so that maximum heat extraction may progress in the air surrounding the expander and be conducted to the internal radiating ribs 123.

Attention is particularly directed to the construction of the expansion tank 122 of Figure X. In this construction the tank is formed in sections consisting of sheet metal rings 125, one edge of which is inturned to form the internal ribs 123 and the other edge of which is outturned to form the external ribs 124. Annular inner channels 126 are also formed adjacent the ribs 124 so that when the sections are superimposed each fits into the other and in this position they are sealed together by a tinning-or similar process to'form the cylindrical casing. The end member 127 is then sealed in the outer end and the end member 128 fixed to the hub member 129 and sealed to the inner end of the casing, thereby completing a sectional assembly which may be readil separated in case access into the chamiier interior is desired. It is, of course, obvious that this structure may similarly be applied to the compressor, and that where the expander is designed to cool a brine solution the outer ribs 124Vmay be omitted as indicated in Figure IX.

Various modifications of the radiating ribs are illustrated in Figures VI and VII. In Figure VI the internal ribs 130 are'lformed with a width increasing inwardly from the cylinder wall to the inner limits of the ribs, the object of this structure being to give -an enlarged radiating capacity as related to the ltotal heat transferred from the cylinder shell. The same formation may be as advantageously applied to the exterior of either compressor or expander when air cooling or radiation is employed. Figure VII illustrates the application of radiating teeth 131 inserted through holes in the cylinder shell and then sealed therein.

Means applicable to all the various modifications of my invention for permitting injection of refrigerant fluid is illustrated in Figure VIII and indicated as applied to the modification of Figure V. In this latter modification the stub shaft 102 is formed with a duct 135 extending to the end thereof, the outer opening being stopped by a screw plug 136. 4As'shown in Figure VIII the section 137 of the shaft is a pulley bearing suitably j ournalled in a support 136 and adapted to receive a pulley (not shown), but in the arrangement of Figure I the shaft is either extended through the motor shaft or a sleeve joint between the section 1'37 and the motor shaft is made. .1

In the description of the various modifications of my invention, I haveindicated the use of a gear pump as the compressing agent. I desire to have it clearly understood, however, that a piston pump may readily be substituted, the weight in such an arrangement, 'carrying the pump andthe drive from the rotating hub to the pump piston being made by means of an eccentric stud extension. In the use ofva piston pump, however, it is desirable to employ an equalizing vali-e in the outlet conduit from the compressor to the expander in order to equalize the pressure when the system is inactive and thus permit ready starting.

n By the use of a gear pump, however, this equalization takes place by leakage around Athe gears thus obviating the use of a separate valve; and for this reason a gear pump in the final form of my invention may be preferred.

Various applications of my invention for refrigerating purposes, may, of course, be made, and the refrigerating unit may be constructed in different sizes as determined by the nature of the application. A desirable application is that, as illustrated in Figure I, whereinv the unit furnishesrefrigeration for domestic purposes and is accordin ly of relatively small dimensions, the unit tting in the upper part of the box. As illustrated the box 150 is divided into four compartments, 151, 152, 153, 154. The outside walls of all compartments, excepting 151, areV formed with an outer layer 155 of wood or metal, a layer'156 of small heat conductivity and an inner metal or wooden layer 157, 'and in addition heat insulating walls are built between the compartments 151 and 154, and between compartment 151 and 152, so that the transfer of heat from .compartments 152, 153 and 154 is slow while that from comparu ment 151 is relatively rapid. The hub of wall between compartments 151 and 152 so that the expansion chamber 11 is wholly within the compartment 152 and heat insulated from the heat producing compressor and motor 20, which, as above indicated are positioned in the nonheat insulated compartment 151. y

The base of compartment 152 is apertured 10 beneath the expander at 157 and adjacent the side wall at 158 and the wall between compartments 153 and 154 is apertured at points 160 and 159 at the top and bottom respectively. A partition 161 is provided depending from the inside of the apertures 158 into the compartment 153 to a distance above the base of the compartment, for the purpose of channeling the circulating air as it moves through the compartments. As indicated by the arrows the air cooled by the brine tank 17 surrounding the expansion chamber, passes through the apertures 158 in the compartment 153, a portion of the cooler air moving into compartment 154 through aperture 159.

The air as it absorbs heat rises, that in compartment 154 passing through the apertures 160 and joining the -heated air in 153 the whole passin through apertures 157 to be recooled by t e brine tank.

By placing the heat producing units in the top of the box 150 the heat not absorbed by the cooling water is carried to the outer walls of the compartment 151 by the heated air where it is radiated into the atmosphere.

In the various embodiments of my lnvention as illustrated and described the operation of refrigeration is basicly similar. Rotation of the unit by the motor 20 is controlled by the thermostat 23 preferably in- 49 serted in the refrigerator box 150. When the box temperature exceeds a predetermined maximum the motor circuit is closed and the unit revolves. Referring to Figure II, when the unit revolves the weight 58 43 holds the gear 51 from bodily movement.

Whereupon the gears by their relative movement create a suction at the inlet 75 and a compression at the outlet 76, thus drawing heated refrigerating fluid from the interior '50 of chamber 11 into the pump and forcing it out under compression into chamberl 10. Thereupon, due to heat. extraction by the cooling water, the fluid assumes a partially liquefied condition and is distributed by the centrifugal force of the rotating drum 10 over the periphery thereof in contact relationship with the outlet pipe 77.

When a difference of pressure between the compression and expander develops after starting, refrigerant Hows through the pipe 77 into the expander where the lower pressure, together with the constantly rising temperature causing a rapid evaporation and resultant cooling. The ribs 80, by providing an inwardly projecting radiating surface not only increased the normal radiating surface, but, as previously indicated, provide means for efficient operation irrespective of whether or not an oil film or layer has accumulated in the tank interior and thus obviates the necessity of an oil separator, a very important consideration. The continued suction Ieffect of the pump draws the vaporized refrigerant together with a small quantity of lubricant back into the compressor thus completing the cycle. The cycle of operation is continuously repeated until the box temperature falls to a point where the thermostat, actuates the switch to open the same when the motor stops and the refrigerant equalizes'its pressure between the two tanks. Attention is directed to the action of the weighted arms 90 as disclosed in the evaporating or expanding chamber 11 of Figure V. The tips ofthese arms which may be slightly scooped shape, cut into the liquid film on a level slightly below the end 108 of the outlet pipe 106. This acts to spray the refrigerant over the internal ribs and throughout the interior of the chamber greatly facilitating and accelerating the refrigeration. Moreover the oil film is broken up so that evaporation may proceed more readily from the liquid film itself if such exists and heat be more readily transferred from the brine or casing exterior to the interior of the chamber without having to pass through the poorly conducting oil film.

Various fluids, such as carbon dioxide, ammonia, or sulphur dioxide, may be utilized as refrigerant in my invention but I have found that sulphur dioxide has advantages in a lower working pressure and some self lubricating properties which makes its use preferred to some extent over the various' other refrigerants.

It is within the intent of my invention to apply the various details and modifications in a manner best suited to the particular application involved or as considered expedient. It is lapparent also that further modifications withinA the scope of the invention may be made. I do not desire therefore, to be limited by the apparatus shown but rather to include all modifications coming within the spirit of my invention and covered by the appended claims.

I desire to claim as my invention:

1. In a refrigerator unit, the combination of a condensing chamber;`an evaporating chamber connected thereto; inwardly projecting ribs secured within the evaporating chamber, said ribs having apertures therethrough adjacent the chamber wall.

2. In a refrigerating apparatus, the combination vof a condenser, an evaporator connected therewith, refrigerating and lubricating liquid within the condenser and evaporator, adapted to form a film on the interior thereof when rotated, a support upon which said evaporator and condenser arerotatably mounted,internally projecting, heat conducting ribs fixed to the interior of said evaporator, said ribs lying ina plurality of parallel planes positioned transversely relative to the axis of rotation of said refrigerating apparatus and penetrating a distance within the evaporator sufficient to extend beyond said liquid film.

3. expansion unit for refrigerating apparatus, said unit comprising a support, a shell mounted for rotation upon said support, and a plurality of heat conducting fins positioned interiorly of said shell, said fins having apertures formed adjacent the inner shell surface adapted to permit free passage of liquid over the interior surface of the shell.

4. A refrigerating apparatus of the character indicated, including a compression tank and an expansion tank hermetically sealed and adapted to be rotated; and compressing means in the compression tank; and a refrigerant and lubricant in said tanks; and means to convey the refrigerant to the expansion tank, said expansion tank being provided with heat transferring fins on the surface of said tank, interiorly thereof, and approximately transverse to the axis of rotation of the tank, and said fins extending appreciably within the tank interior, whereby plural heat conducting areas are formed between the tank interior and exterior.

5. In an apparatus of the character disclosed, comprising a rotary unit including a condenser chamber and an evaporator chamber; a plurality of annular fins extending interiorly from the interior surface of said evaporator chamber to transfer heat to an expanding refrigerant therein from a medium outside the tank to be cooled thereby, said fins having openings therein for the passage of a refrigerant therethrough; and means for effecting agitation of a refrigerant for expansion in said evaporator chamber.

6. In a refrigerating apparatus, a hermetically sealed compression; an expansion tank unit containing a lubricant and a refrigerant, and adapted to be rotated to cause a compression of the refrigerant in said compression tank; a compressor in the compression tank; a conduit connecting the compression tank with the expansion tank; a valve operated by the compressed refrigerant controlling said conduit; means in said expansion tank extending to an appreciable distance interiorly thereof for transferring heat from a medium to be cooled located outside the tank through said lubricant to the interior thereof; and means for transferring refrigerant from said expansion chamber to said compression chamber.

7. In a refrigerating apparatus, the combination of a condenser; an evaporator connected therewith, said condenser and evaporator being adapted for containing a body of lubricant; additional means for transferring lubricant to said condenser. and means including a plurality of continuous annular heat radiating fins within and attached to the wall of said evaporator.

9. In a refrigerating apparatus, the combination of a compressor unit; an expander unit connected thereto; means for cooling liquid compressed by the compressor unit, said expander unit being provided with internal heat radiating projections, said internal projections being apertured adjacent the expander wall to permit axial movement of liquid along the inner surface thereof.

10. In a refrigerating apparatus, an expansion unit therefor, said unit comprising a support; a shell mounted for rotation on said support and forming an evaporator chamber adapted to receive a refrigerating and lubricating liquid; and continuous annular heat radiating projections within and attached to the Wall of said chamber.

11. In a refrigerating apparatus, an expansion unit therefor, said unit comprising a support; a shell mounted for rotation on said support and forming an evaporator chamber adapted to receive a refrigerating and lubricating liquid; and continuous annular heat radiating projections within and attached to the Wall of said chamber, said projections having a maximum width adjacent the bases thereof.

In testimony whereof, I affix my signature.

CARL P. BROCKWAY. 

